Milling machine transmission and control



L. F. NENNINGER ETAL 2,504,443

MILLING MACHINE TRANSMISSION AND CONTROL April 18, 1950 Filed Nov. 15,194:

7 Sheets-Sheet 1 INVENTOR. [f5 TE/PH/Z /W/Ym? Ham A #453 /Y ATTORNEY.

April 18, 1950 L. F. NENNINGER EIAL 2,504,443

MILLING momma: TRANSMISSION AND CONTROL Filed Nov. 15, 1943 7Sheets-Sheet 3 BY 6 o/IJ/ 55/7 /v ATTOR EY.

April 18, 1950 L. F. NENNINGER ETAL 2,504,443

ILLING MACHINE TRANSMISSION AND CONTROL 7 Sheets-Sheet 4 Filed Nov. 15,1943 NNN RN RN MHN Y B WNN NNN N5 Q\ w 5 m9 II H E Q April 18, 1950Filed Nov. 15, 1943 F. NENNINGER EI'AL 2,504,443

MILLING MACHINE TRANSMISSION AND CONTROL 7 Sheets-Sheet 6 ATTORNEY.

April 18, 1950 L. F. NENNINGER ETAL 2,504,443

MILLING MACHINE TRANSMISSION AND CONTROL 7 Sheets-Sheet '7 Filed Nov.15, 19 3 RNN WNW MN MN N H mvmoa F 50/4. #lssm/y ATTORNEY.

Patented Apr. 18, i 1950 MILLING MACHINE TRANSMISSION AND CONTRO LesterF. Nenninger and Fred A. Hassman, Cincinnati, Ohio, assignors to TheCincinnati Milling Machine 00., Cincinnati, Ohio, a corporation of OhioApplication November 15, 1943, Serial No. 510,430

19 Claims.

1 This invention pertains to improvements in machine tools, and moreparticularly to transmissionand control mechanism for milling machines.

One object of this invention is to improve the operation and control ofa milling machine so that the operator at the normal operating positionat the front of the machine may rapidly and conveniently select allchanges in the rate of relative movement between the cutter and work inan increasing or decreasing progressive selection of rate changes by themanipulation of a single operative control lever in a plurality ofoperative .positions determining whether the cutter or the work ratesare to be changed and to effect increasing or decreasing rate changesfor the cutter or for the work.

Another object of this invention is to provide in a knee and column typemilling machine having a speed change transmission in the column and afeed change transmission in the knee, a single, operative control leverconveniently located for manipulation by the operator from the normaloperating position at the front of the machine so as to select whetherthe speed or feed transmissions are to be varied by movement of thelever in one operative position, to effect increasing and decreasingrate changes in the speed change transmission by moving the controllever back and forth in another operative position, and to effectincreasin and decreasing rate changes in the feed transmission by movingthe lever back and forth in still another operative position.

A further object is to provide in a knee and column type milling machinehaving a speed change transmission in the column and a feed changetransmission in the knee, a single lever control to effect increasingand decreasing selections of progressive rate changes in thetransmissions and wherein the drivlngpower from the feed transmission isautomatically disconnected from the work feeding members of the machinewhen the single lever control is operated to effect rate changes in thefeed transmission.

A still further object of this invention is to provide, in a millingmachine having a column and a knee movable on guide surfaces on thecolumn, a, totally enclosed control mechanism located in cooperatingpockets formed in the guide surfaces of the knee and column fortransferring motion from an operating member of the knee to a member tobe controlled in the column for any position of relative movement of theknee on the column.

Further features and advantages of this invention will appear from adetailed description of the drawings:

Figure l is a left hand end elevation of a knee and column type millingmachine incorporating the features of this invention.

Figure 2 is an enlarged view of'the indicating dial showing the spindlespeeds obtained from the machine.

Figure 3 is an enlarged view of the indicating dial showing the feedrates which may be selected for the machine.

Figure 4 is an enlarged fragmentary plan view of the front portion ofthe knee of the milling machine shown in Figure 1, indicating thelocation of the centralized single lever speed and feed rate controllever as it would appear to an operator standing in the normal operatingposition in front of the machine.

Figure 5 is an enlarged fragmentary front elevation of the knee shown inFigure 4.

Figure 6 is a diagrammatic showing of the shiftable gear change speedtransmission for driving the tool spindle.

Figure 7 is a diagrammatic showing of the shiftable gear change feedprovided in the knee of the milling machine.

Figure 8 is a fragmentary section on the line 8--8 of Figures 1, 7 and10, particularly showing the interconnecting mechanism of the singlelever control for initiating the spindle speed changes and the feedchanges and the positioning device for the control lever for its variousoperative positions.

Figure 9 is an enlarged fragmentary section on the line 9--9 of Figures4, 5, 7 and 8.

Figure 10 is an enlarged fragmentary section on the line l0--i llof'Figures '7 and 8;

Figure 11 is an enlarged sectional view seen from the left hand side ofthe machine showing the totally enclosed parallel bar motion transfermechanism on the line ll--ll of Figures 123 and 13. v

Figure 12 is a fragmentary enlarged sectional view of the mechanismshown on the linen-l2 of Figure 11 as seen from the front of themachine.

Figure 12A is an enlarged sectional view on the line l2A--l 2A of Figure12.

Figure 123 is an enlarged sectional view on the line I2Bl2B of Figure11.

Figure 13 is a fragmentary section on the line l3-I3 of Figure 11.

Figure 14 is an enlarged diagrammatic sectional view substantially onthe line |4H of Figure 8.'

Figure 15 is a diagrammatic layout. of the hydraulic control circuit.

For illustrative purposes this novel transmission and control mechanism,for obtaining more elliciently and with greater ease upon the part ofthe operator any desired spindle speed and any desired feed rate from a.centralized single lever control, is shown applied to a. conventionalknee and column type vertical milling machine comprising a base I havingan integral upright column 2 on the upper front portion of which isslidably mounted a conventional vertical spindle housing 3 containing acutter spindle 9|. On

- the front of the column is'molmted for vertical movement on suitableguide surfaces 4, 4a and very great variety as to size and character ofmaterials, necessitating the rapid and easy selection of a great varietyof spindle speeds for the milling cutters and a large variety of feedrates for the knee, saddle and table. Such machines are ordinarily usedon work which would require a large number of changes of speeds andfeeds" for each job for each single piece being machined. As a result itis desirable to provide a relatively simple, conveniently located, andrapidly operable control means for effecting these various speed andfeed changes both during the initial set-up of the job in themachine andduring the multitude of dissimilar operations which are normallyperformed by such a machine as the work is being complemd.

In order to provide an efficient control mechanism of this type themachine is provided, as indicated generally in Figures 4 and 5, with asingle lever centralized control comprising the operating lever l whichis located on the front of the knee 5 of the machine in the mostconvenient location foreasy manipulation by the operator. Generally, thelever It! is operable to a series of four positions: 86a, Mb, We andHid. By specific reference to Figure 4, the lever I0 is arranged to moveto the left into the plane of operation passing through positions 58aand lllb and that by moving the lever to position Illa or "lb 9. seriesof increasing or decreasing speed changes may be effected in the workspindle driving transmission. The lever in is also arranged to be movedinto the plane of operation We and lid to effect a series of increasingor decreasing feed changes in the feeding mechanism of the machine.Thus,- in the single control leveri3 is provided an operative controlwhich in itself can provide increasing or decreasing presentation of allof the spindle speed changes and all of the feed changes that themachine is capable of providing.

Considering now the detailed mechanism for obtaining these desiredfunctions of the machine,

referring particularly to Figure 1, the driving power for the machine isprovided by the main drive motor II, which, through a suitable motorpulley l2 and belts l3 drives the main drive clutch pulley l4 shown bestin Figures 6 and 15. This pulley I4 is rigidly mounted to the sleeve 15by appropriate screws it, which sleeve in turn is journaled in suitablebearings I! in the column 2 of the machine so that it is at all timesconstantly rotated by the main drive motor I 1 during. the operation ofthe machine.

Power for driving the cutter spindle 9| of the 5 machine is obtainedfrom this constantly rotating pulley l4 through a friction clutch shownin Figure 15, comprising a driving plate l8 rigidly mounted on thepulley drive shaft N to which it is attached by a suitable set screw 20.In the 10 sleeve l5 forming an integral part of the driving pulley l 4is out an internal gear 2| in which nicely fits a composition frictionplate 22. This plate may be forced into frictional driving engagementwith the driving clutch plate l8 by the movable clutch plate 23 havingan internal gear 24 formed in its bore uponwhich it is slidingly mountedon a mating gear 25 formed on the fixed member l8.

Conventional toggle actuating means is provided for forcing the plate 23toward the plate Hi to grip the composition disc 22 between them toprovide driving action from the pulley H to the shaft l9. This meanscomprises the swinging toggle arms 26 pivotally mounted on suitable pins2'? in an adjustable yoke 28 carried on the clutch member I8. .Suitablefriction reducing rollers 29 are provided in the ends of these toggles26 to provide ease in operating the clutch mechanism in forcing theplate 23 toward the plate 0 iii. A suitable actuating cam "30 havingtapered surfaces 30a operating on the outer rollers 29 of the toggles 26is mounted by its bore 3| to slide axially on the shaft i9 to cause thetoggles to ride up on the tapered surface 300 of the cam 3|]- forengaging the friction clutch and to allow them to move down on thesurface 30a when disengaging the clutch.

This cam member 30 for operating the friction clutch to engage ordisengage driving power of the pulley l4 relative to the shaft I9 isactuated by a hydraulic servo-mechanism best shown in Figure 15. The cammember 30 is connected-to the push rod 32 through a suitable connectionindicated generally at 33 o that as the rod 32 is moved axially back andforth in a suitable bore 34 provided in the shaft IS the member 30 willthus be operated to elfect engagement or disengagement of the main drivefriction clutch. This,

servo-clutch operating mechanism is of a conventional type shown inPatent No. 1,938,780, issued December 12, 1933, and comprises ahydraulic actuating mechanism including a fluid pressure pump 35 whichsupplies a constant fluid pressure through the line 36 to an annulargroove 31 5 formed in a suitable non-rotating hydraulic connector 38journaled on the surface 39 of the shaft 19. The annular groove 31conveys fluid pressure from the pump 35 through passageways 40 formed inthe shaft I9 which open into a-cylinder bore 4| formed in the pulleydrive shaft l9.

In this bore 4! is slidably mounted a piston sleeve 42 to which isrigidly connected a valve sleeve 43 by means of the pin 45, which lattersleeve 43, in turn, is appropriately rigidly connected through suitablethreaded means 44 to the push rod 32. Also rigidly connected to thepiston sleeve 42 by the pin t5v is the brake operating collar 46 whichhas an abutment surface 41 adapted to be moved into engagement with themultiple disc brake 48 having one group of friction discs rigidly heldagainst rotation in the sleeve 49 rigidly fixed to the column 2 bysuitable screws-50 and the other part of the discs attached to rotatewith the shaft l9. Thus, when 7 this friction brake 48 is operated,rotation of the auoaus shaft I9 will be arrested. The pin" passesthroughaxially disposed slots formed in the shaft I9 to permit axial movementof the pin 45 relative to the shaft l9. When the pin 45 and brakingcollar 40 are in the position shown in Figure the main driving clutchwill be in operation for rotating the shaft l9 and when the collar 46 ismoved to the left to cause its abutment surface 41 to engage the discs48 the shaft I9 will be locked through the friction discs in the braketo column 2 of the machine to thus prevent rotation of the shaft I9.

This mode of operation of reciprocating the push rod 32 and associatedsleeves 42 and 43 is accomplished by hydraulic operating and controlmeans in which the fluid pressure from the passageways enters in theright hand portion sleeve 43 from which it discharges through apassageway 53 into the annular groove 58 of the servo-control valveplunger 55. This valve plunger has fixed on its outer end an actuatingspool 55 which is operated by suitable control lever and linkage meansto be described, for effecting the starting and stopping of the cutterspindle of the machine. It will be noted that a suitable clearance slot51 extending axially of the valve plunger 55 is provided about the pinto permit independent motionof the plunger relative to the sleeve43.

The arrangement shown in Figure 15 illustrates the position of the partsafter the main driving clutch has been put in operation and with thecutter spindle thus being driven from the main drive motor II and thepulley I4. Under these conditions fluid pressure coming out of thepassageway 53 enters into the annular groove 58 of the valve stem 55 butcannot escape out through a passageway 59 into the passageway 60 formedin the sleeve 43 and thus into the left hand chamber 4Ib of the cylinderbore 4| to move the draw rod 32 further to the right, since by holdingthe valve plunger 55 in the desired position shown for full engagementof the clutch the push rod 32 has been moved to the right automaticallyby this servo-movement to cut off the port 59 to thereby bring thefurther movement of the pushrod 32 under fluid pressure to a stop. Nowwhen it is desired to disengage the friction clutch and cause engagementof the brake 48 the spool 55 is actuated by appropriate control meanstothe left, Figure 15, bringing the annular groove SI of the valve stem55 into alignment with the port 59 so as to permit escape of fluidfreely from the chamber 4|b through the passageway 50 and the port 59into the groove .BI from where it goes through passageways 52 into'anaxial bore 63 formed in the valve plunger 55 from which it exhausts toatmospheric pressure to drain back to the fluid reservoir 64 of thehydraulic system. Under these conditions fluid pressure cannot escapefrom the port 53 since it is blocked off at the groove 59 in the valvestem 55 so that the pressure thusbuilt up in the chamber 4Ia of thecylinder bore 4| moves the piston sleeve 42 and its associated sleeve 43and the push rod 32 to the left to thereby disengage the friction clutchand 6 clutch to any-desired-degree. and as fully set forth in the abovePatent No. 1,938,780.

Referring now particularly to Figure 6, there is shown diagrammaticallya change speed gear transmission for driving the cutter spindle of themachine. In this instance power take-off for the spindle change speedtransmission is de rived from the pulley shaft I9, upon which isappropriately mounted sliding change gears 65- 65 and 61 on a suitablesplined driving portion of the shaft I9, and which gears may berespectively engaged with mating gears 68, 59 and I0 to provide in thisillustrative example three speed changes. The gear I0 and a gear II areadapted to be respectively engaged by" gears 12 and 13 of a shiftablecompound gear '|2'I3 to provide two additional speed changes. Additionalspeed changes may be effected by the gearing I4 driving the gear I5which through a clutch engagement at I6 drives the gear I! and a gear I8on a drive shaft I9 and through the gear combinations and 8|, and 82 and83 rendered operative by sliding the shiftable gear N- 83 threeadditional speed changes may be effected in the drive shaft I9. Thus isprovided a series of speed changes in a shiftable gear change speedtransmission for the shaft I9 so that with constant speed rotation ofthe pulley I4 a plurality of speeds may be obtained for the cutterspindle drive by properly shifting the various gears described. Suitablegearing is provided comprising the gear 84 on the shaft I9 which drivesa gear 85 on the shaft 86 and through appropriate bevel gearing 81 andgearing 88 on the vertical shaft 89 which connects with mating gearing90 on the cutter spindle 9|, provides the connecting power transmissionto the cutter spindle in the vertical spindle housing 3.

Feed driving power take-off is obtained from a gear 92, Figures 1 and 6,rigidly mounted on the pulley sleeve I5 so as to be at all times rotatedduringthe operation of the machine by the main drive motor II. This gearis connected to drive a gear 93, Figure 1, rigidly mounted on ahorizontally disposed drive shaft 94 appropriately journaled in thecolumn 2 of the machine. On the forward portion of this drive shaft 94is mounted a bevel gear 95 which in turn drives a mating bevel gear 96on a vertical stub shaft 91 appropriately journaled in column 2 of themachine and upon which is also mounted a gear 98 which is adapted todrive a mating gear 99 having a sleeve portion appropriately iournaledin the column 2 and which sleeve portion has a splined bore I 00 inwhich is fixed the vertical splined drive shaft IN. This splined shaftIOI extends downwardly along the side of the column 2 and has itssplined portion slidingly engaging in driving relationship in anappropriate sleeve I02 journaled against the axial movement in the knee5 so that the sleeve I02 may be at all times driven from the shaft IOIfor any position of vertical adjustment of the knee 5 along the ways 4.

Formed on the sleeve I02, Figure 7, is a gear I03 which, in turn, drivesa mating gear I04 on a stub shaft I05 on which is formed bevel gear I05driving a mating bevel gear I0'I suitably journaled in the knee 5 of themachine. Feed power is taken off from gear I01 fixed on the shaft I 08journaled in the knee and which has a gear I|09 fixed thereon drivingthrough the gears I I0 and I I I the gear I I2 fixed on the input driveshaft III of the change feed transmission, indicated generally at 4.This transmission III has a series of slidingchange gears H6, H6, H1, H8and II! which may be appropriately slid .on their respective shafts intodriving engagement with appropriate meshing gearing so as to provide aseries of feed changes between the input shaft H3 and the output shaft I20 of the feed box II4. Since this type of transmission is ofconventional design, further detailed description of this speciflmechanism will not be undertaken.

n the output shaft I is a gear I2I which, in turn, drives a gear I22 onthe feed drive shaft I23. This shaft I23 may be connected into drivingengagement with or disengaged from the driving gearing which actuatesthe knee in vertical movement, the saddle in cross movement, and thetablein feed movement by the jaw clutch I24. The left hand portion I25of the jaw clutch I24 is connected directly to a driving gear I26 whichdrives a gear I21 on the spline drive shaft I28 which through suitableconventional gearing is adapted to drive the table feeding movement ofthe machine. Appropriate means, not shown, are provided between theshaft I28 and the table movement for connecting or disconnecting thedriving power therefrom.

The gear I21 also drives a gear I29 and, through suitable reversingmeans, a gear I39 which latter gears may be connected alternately bymeans of a suitable reversing clutch I3I to rotate the saddle crossfeeding screw I32 in either direction, or to disconnect the drivingpower therefrom. Similarly, a gear I33 is driven from gear I21 throughthe gear I23 and the gear I34 is driven from the gear I30. By means ofan appropriate reversing clutch I35 and associated conventional gearingnot shown reverse drive to the shaft I36 or ar resting of power to theshaft may be effected. The shaft I36 is connected by appropriate meansI360, to the vertical elevating screw I361) of the knee for effectingvertical motion therein.

The spindle change speed gear transmission is controlled by power meanswhich. shifts the various sliding gears in a predetermined sequentialrelationship to provide a series of progressive speed changes from thelowest to the highest speeds. In Figure 6 is diagrammatically shown theessential elements of such power gear shifting mechanism comprising agear I31 fixed on the pulley sleeve I5 to bethereby continuously rotatedat all times during the operation of the machine by main drive motor II.This gear I3! drives a gear I38 which through appropriate transmissionmechanism, indicated generally at I39, drives a pair of reversing bevelgears I40 and MI, which may be alternately connected to reversibly drivea shaft I42 by a suitable reversing clutch I43 so as to rotate the shaftI42 in one direction or the other as desired. On the shaft I42 is fixedan appropriate gear I44 which drives another gear I45 for rotating thefluid pressure selector valve I46 which effects the proper sequentialshifting of the gears in the spindle transmission of Figure 6. Theselector valve I46 may be'connected to the various shiftable gearspreviously described by conventional fluid pressure actuated cylinders.Also an appropriate indi= cating dial I showing the actual speedsselected as the control valve I46 is thus driven by power in onedirection or the other by actuating the clutch I43, is showndiagrammatically as driven from the spiral gear I41 rotated with thecontrol valve I46 which drives the spiral gear I48 on the dial shaft I49which carries the spindle speed indicating dial I66.

. I14 in the knee'5 by the set screw I14a.

m, Figure '1, for effecting the power means. Power for effecting thisoperation of the shifting of the feed transmission gearinl is derivedfrom a bevel gear I6I driven by the shaft I08 which, in turn, drives amating bevel gear I52 on a shaft I53. On the shaft I63 is provided asuitable worm I64'which drives a worm wheel I55 formed on a bevel gearI66 which bevel gear I56 drives an idler bevel gear I61 in turn adaptedto drive another bevel gear I68 similar to the bevel gear I66. Anappropriate law clutch I59 may be connected to one or the other of thebevel gears I66 and I68 so as to cause the driving of the shaft I66 inone direction or the other as desired. This shaft I60 has a. gear I6Iwhich, in turn, drives a gear I62 for rotating the gear shifting camdrum I63 and through the gears I64 and I65 the gear shifting cam drumI66. Appropriate dial indicating means I61 carried on a. suitable shaftI58 and driven appropriately through the mechanism I69 from the gear I62indicates the relative positions of the cam drums I63 and I66 and.therefore the positions of the gears in the feed box transmission H4 andthe feeds selected. Conventional shifter arms I10 operating inconjunction with appropriate cam slots in the cam drums I63 and I66provide means, when the cam drums are rotated, to actuate the ears ofthe transmission H4 in their proper sequential rela-v tionship.

Each of these power actuating mechanisms for effecting the sequentialshifting of the gears in the spindle change speed transmission and inthe feed change gear transmission are effected from the common operatingand control lever I4, Figures 4 and 5, when moved to the respectiveoperating positions Ilia and I01 for spindle speed changes and I60 andIM for feed changes as set forth above. In Figure 9 is shown theoperating handle I8 havin an integral ball portion I1I fitting in a boreI12 of a sleeve I13 fixed in the bore This ball portion is provided witha tangential slot I16,

Figure 5, which nicely fits each s ide of bail-' pointed pin I16 fixedin the outer rim portion of the sleeve I13 so that the handle ma beswung in and out relative to the front of the knee 6 while its ballportion I15 rocks the slot I16 around the ball-pointed pin I16while'rotating in the bore I12 of the sleeve I13 to thereby similarlymove a pivot pin I11 carried in the ball portion "I. To this pin I11 isattached the rocking and swinging rod I18 so that in and out motion ofthe handie I0 effects axial sliding in and out motion in the shaft I18,and rotation of the handle about the axis of the shaft I18 rocks thisshaft about its axis. In this way the shaft I18 is given a combinationof axial and rocking movements from the single control handle III bymoving it to the respective positions shown in Figure 4.

The shaft I18 is appropriately supported at its inner end by a suitablebearin I19 formed in the Similarly, the change speed gear transmission76 knee 5. This shaft I18 has fixed on its inner end a shifting yoke I88best seen in Figures '1, 8 and 14, which may be swung into an operatingnotch I8I formed in the actuating plunger I62 for spindle speed changesand into an actuating notch I83 formed in the shuttle valve plunger I64of the shuttle control valve I86 when effecting feed changes for theknee, saddle, and table, by the sidewise swinging of the lever II fromthe respective positions IIJcI6b and I6cI6d shown in Figure 4. Theserelative positions of insertion various feed changes in the knee alsohas its gears shifted in a predetermined sequential relationship by ofthe yoke I88 with respect to the operating notches I8I and I83 in theplunger I82 and in the shuttle valve plunger I84 are diagrammaticallyshown in Figure 14 for the corresponding positions of the control levershown in Figure 4.

Normally the side faces I86 and I81 of the yoke I80 nicely fit betweenthe positioning pins I88 and I89 to permit free rocking motion sidewaysof the lever I8 from position Ia-I8b or to position I8c--I8d. When thecontrol lever I8 is moved to the speed selecting position, i. e., swungto the left into the position I0a--I8b its end face I98 swings into theslot I8I of the plunger I82 to thereby connect the handle I0 for axialmovement of the plunger I82. The plunger I82 is normally centralized inits axial movement for proper entry or withdrawal of the yoke I80 whenno speed changes are being effected by a spring I 8a, Figure 10, whichbears against the knee through a washer I82b at one end and at the otherend through a washer I 82c which can also engage the bearing bushingI82d fixed in the knee 5 and a collar I82e fixed to the plunger I82. Itwill therefore be obvious that the plunger ma be moved axially in eitherdirection, compressing the spring I82a, which will cause return of theplunger to a central position when released b the yoke I88. At this timethe shifting yoke I88 has moved out from between the positioning pinsI88 and I89 so that its surface I9I is free to pass these pins andassume a position I80a with the handle moved toward the knee of themachine for institutin the increasingspeed changes and into positionI88b for instituting decreasing series of speed changes. In either ofthese positions the surface I9I is respectively behind the pin I88 orI89, Figure 14, so that the lever cannot return to the central positionuntil it is midway between the selecting positions I0a and I 8?). A pairof stop pins I93 and I94 are also provided which engage the side facesI88 and I81 of the shifting yoke I88 to limit the axial movement thereofand the shaft I18 for accurately positioning the handle I0 in either ofthe positions I8a or I8b.

.When the lever I8 is swung to the right to effect feed changes, thesurface I9I of the shiftin yoke I80 moves into the actuating slot I83 ofthe shuttle valve I 85 so as to connect the handle I0 to the feedchanging control mechanism. Under these latter conditions the shiftingyoke I88 is swung between the positioning pins I88 and I89 but the yokeI80 is permitted axial movement and likewise the shaft I18 can moveaxially since there is a clearance slot I92 formed therein so that thepositioning pins I88-I89 are straddled by the slot when the shiftingyoke is in the relative positions I880 and I88d corresponding to thepositions I80 and I0d of the control lever I0.

In order normally to keep the handle I8 in the central positionindicated at I8 in Figure 4 and with the shifting yoke I80 in theposition shown in Figure 8 and in full line in Figure 14, a centralizingspring arrangement shown best in Figure 8 is provided, comprising asmall depending integral lug I95 formed on the shifter yoke I88 fixed tothe shaft I18 which operates between a pair of spring urged collars I98slidably mounted on a suitable stud I91 fixed to the knee 5 of themachine. A pair of springs I98 each side of the sleeves I98 andrespectively engaging against the fixed portion of the knee of themilling machine through the medium of the fixed collar I99 on the studI91 and directly against the mounting means on the knee 5, providesmeans for normally keeping the handle in central posi- 10 tion whilepermitting rocking movement of it to any of the desired selectablepositions I8a--I8b or I8c-I8d, while at the same time providingautomatic return of the handle to the central position when released bythe operator.

When the lever is swung to the left into the operating position I0a--I0band the shifting yoke I88 is in the slot I8I of the plunger I82,movement of the control lever I8 into either position I8a or I0b causessliding motion in the plunger I82 which is transmitted through a lever288 pivotally mounted on a suitable pin 28I in the knee 5 and which hasan appropriate lug 282 operating in a slot 203 in the plunger I82 andhas a similar lug 204 on its other end which operates in a correspondingslot 285 in the shifter rod 288, which is slidably mounted in the knee5. This rod 206 extends to the rear of the knee and projects outwardlypast a parallel motion bar arrangement for conveying motion of the rod286 at all times to mechanism in the column 2 for any relative verticalposition of the knee 5 on the column.

This parallel motion transferring mechanism, Figures 11, 12, 12A, 12Band 13, comprises a bar 281 which is pivotally mounted on the pins 288of a pair of crank arms 289 which in turn are pivotally mounted onsuitable pins 2I8 in a pocket 2I8a formed in the guideway surface 40 ofthe knee of the milling machine, Figure 12B, so that as the bar 201 ismoved back and forth horizontally it will remain in vertical parallelismduring such movement. In order to maintain a high degree of accuracy ofthis parallel movement a supplementary tie bar 2 is provided which ismounted on pins 2I2 on the crank arms 288 so that the relationship ofthe pivots 288 2I8 and 2I8--2I2 lie in planes substantiallyperpendicular to each other to in this way minimize irregular motionwhich might otherwise be caused in the parallel bar 201 when pushed atone or the other of its extreme ends.

The shifter rod 286 is adapted to horizontally push or pull the parallelbar 281 to effect its parallel motion, Figure 13, by providing in thebar a slot having the side faces 2I4 which nicely engage mating surfaces2I3 formed on the bar 281, while permitting limited up and down motionof the bar 281 relative to the shifter rod 286 during the actuation ofthe bar 281 in parallel motion.

Reciprocation of the bar 286 by the handle I8 causes similar motion inthe parallel bar 201 which is conveyed to the lever arm 2 I5, Figure 6,carried on a rock shaft 2I6 in the column 2 by a pin 2" fixed in the endof the lever. This pin nicely fits in the longitudinally extending slot2 I8 formed in the parallel bar 281.

It is to be noted, with particular reference to Figures 11 and 123, thatthe lever 2I5 and pin 2I1 are contained in a pocket 2 Ilia formed in theguideway surface 4a of the column 2. The two pockets 2I8a and 2I6a arecooperatively positioned relative to each other so as to form a chamberfor at all times totally enclosing the parallel bar motion transfermechanism for any position of movement of the knee 5 or the column 2.

Rocking motion from the shaft 2I8 is conveyed through a suitable leverarm 2I9 fixed thereto which actuates a push rod 228 slidably mounted inthe column 2 and which has a suitable shifter yoke 22I operating theshifter spool 222 of the clutch shifting rod 223 for actuating the jawclutch I48 to engage it with either bevel gear I48 11 or bevel gear I.Thus, as the control lever I8 is moved either into position No or I 8b,one or the other of the clutches I48 or I will be engaged to effectrotation of the hydraulic gear shifting selector valve I46 in onedirection or the other to effect the various gear changes in the spindlespeed transmission. The operator in manipulating the handle I8 in thesepositions need only watch the indicating dial I58 to see what speed isbeing selected, and since it may be rotated in either direction throughthe medium of the clutch I43 and associated reversing bevel gearingI48I4I, the range of speeds may be selected progressively at increasingrates or progressively at decreasing rates as desired and also thechange from the highest range to the lowest range or vice versa may alsobe instantly effected. A supplemental control lever 224, Figures 1 and6, carried on a rock shaft 225 mounted in the column 2 and having alever 226 fixed thereon and operating with the push rod 228 in the samefashion as the lever 2I9 above described provides manual control meansfor effecting speed changes in the spindle speed transmission from acontrol lever located on the column 2 of the machine.

When the control lever I8 is moved into the positions Me or IM foreffecting feed changes for the knee, saddle and table members, theshifter yoke I88 is swung into the notch I83 in the shuttle valve I84 sothat this valve may be reciprocated manually in the sleeve I85 of saidvalve. Normally, after the desired spindle speed and desired feed havebeen selected and with the control lever I8 in the central positionshown at I8 in Figure 4, fluid pressure from a suitable fluid pressurepump 22'! is derived from the fluid pressure reservoir 64 through a line228 and is delivered under pressure through a line 229 to the port 238in the sleeve I85 of the shuttle valve I84 and is discharged through thelines 22 and 232 into the respective cylinder chambers 233 and 234 ofthe hydraulic actuating means for operat-' ing the clutch I59 for thepower shifting of the feed change speed transmission. In each of thecylinders 233 and 234 are slidably mounted the sleeve pistons 235 and238 inside of which also slides the shifter yoke piston rod 231 to whichis attached the shifter yoke 238 connected to the clutch I59. Underthese conditions of the simultaneous application of fluid pressure toboth cylinder 239 and 234 the sleeve pistons 235 and 236 will both beprojected toward each other as shown best in Figure so as to confine themovement of the shifter yoke 238 between them to centralize the clutchI59 in inoperative position. Thus, no shifting of the feed transmissionis taking place under these conditions.

When the control lever I8 is moved into one or the other of thepositions I8c or IIld the shuttle valve plunger I84 will be so moved toat one time connect the fluid pressure from line 229 and port 238 toline 23l to apply pressure to the cylinder chamber 233 while connectingthe line 232 from the cylinder chamber 234 to the exhaust drain line 239returning exhausted fluid to the reservoir 64. When the lever I8 ismoved to the other position the valve will be shifted in the oppositedirection to apply pressure to the line 232 into the cylinder chamber234 and permit exhaust fluid to escape from the cylinder chamber 233 tothe drain line 239. It can be seen that when pressure is applied only inone of the cylinder chambers 233 or 234 the rod 231 will be moved byfluid pressure toward the exhausting cylinder chamber and will likewisecarry with it the re- 12 spective sleeve 235 or 288 to permit movementand the corresponding engagement of the clutch I" with one or the otherof the beveled gears I88 or I55 to thereby institute the power drivingof the gear shifting mechanism for the feed change transmission in onedirection or the other.

The feed changes may also be effected by a rear control lever 248,Figures 1 and 15, mounted on the knee of the machine to the rear of thework table for actuating the shuttle valve I84 in either direction byfluid pressure in addition to the mechanical actuation of the valve bythe lever I8 as previously described. Pressure is derived from the line229 which is connected to a control valve 24I appropriately operatedthrough suitable linkage 242 from the control lever 248 whichreciprocates this plunger 243 to at one time connect fluid pressure fromthe pressure line 229 through the line 244 into a chamber 245 at one endof the shuttle valve sleeve I85 and to connect the other chamber 246 atthe other end of the valve I84 through the line .241, through the valve24I, to the exhaust line 239 so asto move the shuttle valve sleeve inone direction. The reverse move- -ment of the valve I84 may be readilyeffected by actuating the valve 2 in the opposite direction by the lever248 whereupon fluid pressure in the line 229 is then conveyed throughline 241 to the chamber 246 of the valve I84 while exhaust fluid isconveyed from the chamber 245 through the line 244, the valve 2 into thedrain line 239. Suitable spring urged centralizing means shown generallyat 248 serve to normally keep the valve 2 in a central inoperativeposition with no pressure being applied from line 229 to either of thelines 244 or 241. The shuttle valve I84 is also normally maintainedcentralized by the springs I850. in the position shown in Figure 15 whenno pressure is applied in either chamber 245 or 246.

The servo-operated spindle clutch and brake mechanism, Figure 15, iscontrolled from an operating lever 249 mounted on a suitable rock shaft258 on the front of the knee as shown in Figures 1, 4, and '7 which hasa suitable projecting lug 25I which operates an appropriate notch in theactuating rod 252, Figure 7, which extends to the rear of the knee,similar to the rod 286, and is similarly attached to a second parallelmotion operating bar 253, Figure 11, which is mounted on suitable crankarms 289 as is the member 281 to in this way convey movement of thecontrol rod 252 to mechanism in the column for any relative verticalposition 'ofthe knee thereon. A suitable lever arm 254, Figure 6, havinga pin 255 operating in the vertical slot 256 in the parallel motion bar253 is carried on a rock shaft 251 to which is fixed the shifter arm 258properly connected to the actuating spool 56 of the hydraulicservoclutch and brake operating mechanism shown in Figure 15. A similarcontrol lever 259 is also provided on the side of the column of themachine on a suitable rock shaft 268 and througha suitable lever 26l andthe shifter rod 262 and the lever arm 263 fixed on the rock shaft 251provides a control on the column operable in conjunction with thecontrol lever 249 on the front of the knee. Manipulation of either ofthese levers 249 or 259 controls the operation of the hydraulicservo-clutch and brake mechanism for starting or stopping spindlerotation.

Means are provided in connection with the conchanges can be effected.This mechanism comprises an interference detent arrangement, Figure 6,comprising a ball detent 264 carried in the column 2 to position theservo-clutch control rod 262 normally in the disengaged position of themain drive clutch I4 and a second ball detent arrangement 265 carried inthe column to provide means for normally positioning the control rod 226in cooperation with the centering spring I82a in the knee, Figure 10,for rendering the power gear shifting mechanism for the spindle speedtransmission normally inoperative. Between these two bars is alsoprovided an interference ball detent 266 which permits the operation ofeither the rod 262 or the rod 228 only when one or the other is in thenormal position as determined by the respective detents 264 or 266. Inother words, the rod 228 cannot be moved in either direction to effectengagement of the clutch I43 unless the rod 262 of the servo-clutchoperating mechanism is positioned in the disengaged position of thedriving clutch in the pulley I4. Likewise when the rod 228 is in one orthe other of its positions of clutch engagement of the clutch I48 of thebevel gears I48 or I the servo-clutch control rod 262 and associatedmechanism cannot be moved from the disengaged position as to prevent thespindle from being inadvertently started during speed changes in thespindle speed transmission.

when feed changes are to be selected, means is provided forautomatically disconnecting feed 'power from the work table, saddle andknee so as to effect the changes of speed in the feed transmission whenno feeding loads are imposed thereon. This mechanism is illustrated bestin Figure which shows the positions when the machine is in normaloperation with the spindle running and no speed or feed changes beingmade. Under these conditions, fluid pressure from the line 229 comingfrom the fluid pressure pump 221 passes through the shuttle valve I86into the line 261, through the spindle stop control valve 268, into theline 269 connected to the actuating cylinder chamber 210 in whichoperates the feed clutch shifter piston 21I to which is connected ashifter yoke 212 properly connected to the shlftable feed clutch I24.Exhaust from the cylinder chamber 213 which carries the other end of thepiston 21I is conveyed through the line 214 through the valve 268 intothe line 215, and through the shuttle valve I84, into the drain line 239so that normally fluid pressure is applied in the cylinder 218 tomaintain the feed clutch I24 in engagement with its mating member I25 tomaintain feed drive power to the knee, saddle, and table elements whenthe spindle is running.

when the control lever III is moved to either of the positions IIIc orIild for initiating feed changes, the shuttle valve will be so moved asto apply pressure in each case from the line 226 to cylinder 218 throughline 215, the valve 268, and through line 214 to move the piston 21I tothe right, Figure 15, to thereby disengage the feed clutch I24. When thehandle I8 is again allowed to come back to neutral position, the shuttlevalve will again resume the position in Figure 15 to initiatereengagement of the feed clutch I24 by the application of pressure inthe cylinder 218 by connecting pressure from line 229, through line 261,valve 268, and line 269. Under these conditions, the control valve 268is in the released normal running position with its plunger 2" in thedepressed position as shown in Figure 15. Thus is provided automaticmeans for disconnect- 14 ing feed driving power from the change feedtransmission when selecting any feed changes and to automaticallyreengage the feed drive powerwhen the desired feed has been selected.

It is also the purpose to provide an arrangement in conjunction withthis transmission and control mechanism whereby the feed drive power isautomatically disconnected whenever the cutter spindle drive is stoppedin order to prevent an otherwise continuation of the feed of the workpiece against the cutter when not rotating, resulting in obvious damageto the machine mechanism. The spindle control valve 268 having theplunger 21 I which is shown in normal depressed running position inFigures 10 and 15, has its plunger actuated by a cam 212' fixed to therock shaft 261 of the hydraulic servo-operated drive clutch operatingmechanism. When the servoclutch is operated by manipulating levers 249or 259 to stop spindle rotation as in swinging the rock shaft 251clockwise from the run position to the stop position, the valve plunger2" will be moved under the influence of the spring 266 to permit fluidpressure from the line 228 to pass through the valve 268, into the line214 whereby pressure is applied to the feed clutch cylinder 213 todisengage the feed clutch I24. Exhaust fluid from the cylinder 21!!passes out through line 268, the valve 268, and into the drain line 239appropriately connected to the valve 268 for return of fluid to thereservoir 64.

Similarly, when the spindle drive is again reengaged by operating thecontrol levers 249 or 258 the valve 268 will have its plunger moved downto the position shown in Figure 15 to again automatically reengage feedclutch I24. Then, whenever the spindle rotation is stopped, the feedtransmission H4 is automatically disengaged from the work table, saddle,and knee members.

What is claimed is:

1. In a machine tool, having a rotatable spindle and a feeding member, achange speed transmission for said spindle and a change feedtransmission for said feeding member, a power means for effecting thespeed changes in said first-mentioned transmission and a second powermeans operable to effect feed changes in said secondmentionedtransmission, a common centralized control mechanism for rendering saidpower means selectively effective comprising, a single operating controllever having a neutral position and shiftable into and movable in oneplane of movement for effecting increasing or decreasing speed changesin said first-mentioned transmission and operably shiftable into andmovable in another plane of movement to effect increasing or decreasingfeed changes in said feed change transmission, a main drive motor fordriving both of said transmissions and said power means for effectingthe speed changes therein, means for disconnecting driving power fromsaid main drive motor to said change speed transmission when changes ofspeed are being effected therein, means operable by said single controllever for disconnecting power from said change feed transmission to saidfeeding member when feed changes are being effected therein, andadditional means for disconnecting said feed transmission from saidfeeding member when said main drive motor is disconnected from saidspeed transmission.

2. In a milling machine, a column, a knee mounted on said column havinga saddle and work table, a cutter spindle, a change speed transmissionfor effecting a plurality of different rates of rotation for said cutterspindle, a main drive motor for driving said transmission, a change feedtransmission for actuating said knee, saddle, and table at a pluralityof feeding rates, means for driving said change feed transmission fromsaid main drive motor, a single operative control member mounted on thefront of said knee operable to selectively effect speed changes in saidcutter spindle transmission and to efiect feed changes in said feedtransmission for the knee, saddle, and table, a control lever on saidcolumn operable in conjunction with said single lever control foreffecting speed changes in said cutter spindle transmission only, acontrol lever on the rear of said knee operable in conjunction with saidsingle lever control to effect only feed changes in said feedtransmission for the knee, saddle, and table, and interlock means toprevent simultaneous actuation of the control levers reacting on saidsingle lever control, said lever for said spindle speed changes and thelever for said feed changes, whereby only one of said three levers maybe operated at any one time.

3. In a machine tool transmission and control mechanism, a rotatablespindle, a change speed transmission associated with said spindle, aprime mover for driving said transmission and spindle, a feeding member,a change speed transmission associated with said feeding member, meansfor drivin said change feed transmission from said prime mover, meansfor connecting or disconnecting said prime mover from drivingrelationship with said change speed transmission, fluid pressure meansfor operating said connecting and disconnecting means, means forcontinuously connecting said prime mover to said change feedtransmission, connecting and disconnecting means between said changefeed transmission and said feeding member, fluid pressure means foroperating said second-mentioned connecting and disconnecting means, a'fluid pressure selector valve movable in opposite directions, foreffecting increasing and decreasing speed changes in said change speedtransmission, power means for effecting feed changes in said change feedtransmission, a fluid pressure shuttle control valve movable in oppositedirections for feed increases and decreases, said valve being operableto control the power feed changing means for said feed transmission andfor connecting and disconnecting said feed change transmission relativeto said feeding member in a predetermined sequential operation in whichsaid feed transmission is disconnected from driving said feeding memberwhen said shuttle valve is operated to effect feed changes in saidtransmission, and a single lever "control mechanism selectively operableto actuate the fluid pressure selector valve in said opposite directionsfor effecting speed changes in the change speed transmission or toactuate said shuttle control valve in said opposite directions foreffecting feed changes in said feed transmission.

4. In a milling machine, a column, guideways on said column, a kneehaving cooperating guideways thereon, control means on said knee,mechanism to be controlled in said column, parallel bar motion transferapparatus located in an elongated pocket in a guideway of said kneeextending in the direction of relative movement of said knee on saidcolumn, means located in a pocket in a cooperating guideway of saidcolumn for connecting motion from said parallel bar apparatus to saidmechanism to be controlled, said pockets in said knee and columnguideways being so arranged as to form a structure totally enclosingsaid parallel bar transfer mechanism for any position of said kneeonsaid column. 1

5. In a change speed transmission and control mechanism for a millingmachine, a change speed transmission for operating the tool spindle at aplurality of different speeds, a change feed transmission for operatinga feeding member at a plurality of feed rates, a single lever controlhaving separate operative positions to determine selectively the speedor feed transmission to be controlled, independent controllers for saidtransmissions engageable by the lever, said lever when selectivelypositioned being movable into additional operative positions, therebyactuating the selected controller to effect increasing or decreasingrates of selected speeds respectively in the change speed transmissionor the change feed transmission, and reversible power means including anindividual reverser coupled with each controller and rendered operativeby the movement of said single lever and the selected controller in saidlast-mentioned operative positions for effecting respectively increasingand decreasing rate output changes as respects the selected of saidtransmissions.

6. In a machine tool organization including a support member having aspindle rotatably mounted therein and a variable speed transmission foreffecting rotation of said. spindle, a-

work supporting member movable with respect to the spindle and having avariable speed trans-' mission mounted therein for effecting saidmovement, separate power means including independent reversers foreffecting rate changes in said variable speed transmissions,juxtapositioned controls for said power rate changers carried by themovable member, said controls each being shiftableto operate one of thereversers and to effect both increase and decrease of the output rate ofits associated variable speed transmission, a single control membercarried by the movable member, and means mounting said control memberfor initial selective movement to engageone or the other of thejuxtapositioned controls and for subsequent movement when in a selectedposition to shift a selected control to effect alternative increases ordecreases in theoutput rate of its associated transmission.

7. In a machine tool organization including a support member having aspindle rotatably mounted therein and a variable speed transmission foreffecting rotation of said spindle, a work supporting member movablewith respect to the spindle and having a variable speed transmissionmounted therein for effecting said movement, separate power means foreffecting rate changes in said variable speed transmissions,juxtapositioned controls for said power means carried by the movablemember, said controls each being shiftable to effect alternativelyincrease or de-"' crease of the output rate of its associated controlledpower rate changing means, a single control member carried by themovable member, and

' means mounting said control member for initial selective movement toengage one or the other of the juxtapositioned controls and forsubsequent movement when in a selected position to shift a selectedcontrol to effect increases or decreases in the output rate of itsassociated transmission, one of said juxtapositioned controls comprisinga hydraulic valve member in direct hydraulic connection with one of thepower shift mechanisms for determining the operation thereof and theother of said controls comprising 17 mechanically shiitable elementsmovable in accordance with the shifting of the singlecontrol member.

8. In a machine tool organization including a support member having aspindle rotatably mounted therein and a variable speed transmission foreffecting rotation of said spindle, a work supporting member movablewith respect to the spindle and having a variable speed transmissionmounted therein for effecting said movement, separate power means foreifecting rate changes in said variable speed transmissions,juxtapositioned controls for said power rate changers carried by themovable member, said controls being shiftable to effect both increaseand decrease of the output rate of the variable speed transmissions, asingle control member carried by the movable member, means mounting saidcontrol member for initial selective movement to engage one or the otherof the juxtapositioned controls and for subsequent movement when in aselected position to shift a selected control to eifect increases ordecreases in the output rate of its associated transmission, one of saidjuxtapositioned controls comprising a hydraulic valve member in directhydraulic connection with one of the power shift mechanismsfordetermining the operation thereof, and means for alternativelydetermining the position of said hydraulic valve including a reversiblehydraulic circuit, a reversing valve member for controlling the flowthrough said hydraulic circuit, and means remote from the first controlmember for selectively determining the position of the reversing valveand thus the reaction of the hydraulic circuit on the firstmentionedvalve.

9. In a machine tool organization including a support member having aspindle rotatably mounted therein and a variable speed transmission foreffecting rotation of said spindle, a work supporting member movablewith respect to the spindle and having a variable speed transmissionmounted therein for effecting said movement, separate power means foreffecting rate changes in said variable speed transmissions,juxtaposition controls for said power rate changers car ried by themovable member, said controls being shiftable to effect both increaseand decrease of the output rate of the variable speed transmissions, asingle control member carried by the movable member, means mounting saidcontrol member for initial selective movement to engage one or the otherof the juxtaposition controls and for subsequent movement when in a,selected position to shift a selected control to effect increases ordecreases in the output rate of its associated transmission, one of saidjuxtapositioned controls comprising a hydraulic valve member in directhydraulic connection with one of the power shift mechanisms fordeterminin the operation thereof and the other of said controlscomprising mechanically shiftable elements movable in accordance withthe shifting of the single control member, and means for alternativelydetermining the position of said hydraulic valve including a reversiblehydraulic circuit, a reversing valve member for controlling the flowthrough said hydraulic circuit, and means remote from the first controlmember for selectively determining the position of the reversing valveand thus the reaction of the hydraulic circuit on the first-mentionedvalve, an additional remotely situated control lever, and operativemotion transmitting connections between said control lever and themechanical shifting mechanism selectively engageable by thefirst-mentioned control member for alternatively actuating saidmechanical shifting means.

10. In a change speed transmission and control mechanism for a machinetool, a change speed transmission for operating a spindle at a pluralityof different speeds, a change feed transmission for operating a feedingmember at a plurality of feed rates, independent power controls eachincluding an individual reverser for determining alternatively increasesor decreases in the respective output rates of said transmissions, afirst joint control member selectively movable into operative relationwith-one or the other of said power controls and subsequently operableto react thereonto produce either said increases or decreases intheoutput rate of the selected transmission control, and separate remotecontrols individual respectivelyto each of said power means forindependently determining rate changes in the respective transmissions.

11-. In a change speed transmission and control mechanism for a machinetool, a change speed transmission for operating a spindle at a pluralityof difierent speeds, a change speed transmission for operating a feedmember at a plurality of feed rates, independent power means foradjusting said transmissions to effect increases and decreases in theultimate speed and feed rates transmittable thereby, and control meansfor said transmission adjusting mechanisms includin independentre'versers, juxtapositioned controllers individual to the respectivereversers, and a single control lever supported intermediate saidjuxtapositioned controls and selectively oscillatable into actuatingengagement with one or the other of said controls, said lever beingmounted for additional oscillation in a second direction to shift theselected reverser control to eifect increasing or decreasing rates ofselected speeds in its associated transmission.

12. In a machine tool transmission and control mechanism, a shi'ftablegear change speed transmission for driving a member at a plurality ofdifferent rates, a prime mover for actuation of said transmission,clutch means for controlling the coupling of the prime mover to thetransmission, power shifting means for effecting changes in the ratetransmittable by I the change feed transmission, a reverser fordetermining the directional actuation of said power shifting means,hydraulic motors for determining the position of the coupling clutch andof the reverser, a source 13. In a machine tool of the type embodying arotatable spindle and an element translatable with respect to saidspindle, transmission and control mechanism for said parts including anactuator for the spindle, a controller for determining the coupling ofthe actuator with the spindle, an organized variable speed transmissionfor actuation of the translatable member, clutch means for determiningthe operative coupling of said transmission, a power adjuster for saidtransmission, a hydraulic control system or said parts including asource or actuating medium, a hydraulic motor for determining theposition of the clutch, serially disposed valve elements intervening thesource and motor, an actuator for shifting one of said valve elements toactuate the motor for disconnection of the clutch,

and means operable by the spindle controller for actuating the other ofsaid valve elements to effect corresponding actuation of said clutchmem- Id. In a machine tool of the type embodying a rotatable spindle andan element translatable control mechanism for said parts including anactuator for the spindle, a controller for determining the coupling ofthe actuator with the spindle, an organized variable speed transmissionmeanstoactuateeameasthevalveisshlftedan additional hydraulic actuatoralternatively operable to shift saidvalve element, and means operable bythe spindle'controller for actuating the other oi said valve elements toeflect corresponding actuation oi said clutch member.

17. The combination with an organized variable speed transmissionioramachine tool or the like and a prime mover ,i'or actuation of saidtransmission, of a clutch element for operatively connecting the primemover and said transmission, power means for 'efleoting shifting of thewith respect to said spindle, transmission and for actuation of the,translatable member, clutch means -for determining the operativecoupling of said transmission, a power adjuster for said transmission, ahydraulic control system'ior said gears of said transmission to increaseor. decrease the rate transmittable thereby, driving means for saidpower shifter including a reverser, a first hydraulic motor for,eflectlng disconnection or the transmission clutch,-a second hydraulicmotor for eftectin opposite directional couplings of the reverser, ahydraulic control system for said motors parts including a source ofactuating medium, a l

hydraulic motor for determining the position of the clutch,- seriallydisposed valve elements intervening the source and motor, an actuatorfor shifting one of saidvalve elements to actuate the motor fordisconnection of the clutch, an additional hydraulic actuatoralternatively operableto shift said valve element, andmeans operable bythe spindle controller for actuating the other of said valve elements toeflect corresponding ace tuation of said clutch member.

15. In a machine tool of the type embodying a rotatable spindle and anelement translatable with respect to said spindle, transmission andcontrol mechanism for said parts including an actuator for the spindle,a controller for deter- ,mining the coupling of the actuator with thespindle, anorganized variable speed transmission for actuation of thetranslatable member, clutch means for determining the operative couplingof said transmission, a power adjuster for said transmission, ahydraulic control system for said parts including a source of actuatingmedium, a.

hydraulic motor for determining the position of the clutch, seriallydisposed valve elements intervening the source and motor, an actuator,for shifting one of said valve elements to actuate the motor fordisconnection of the clutch, control means for the power adjuster,means'in the valve to selectively couple the source with the conblespeed transmission for a machine tool or the trol means to actuate sameas the valve is shifted,

and means operable by the spindle controller for actuating the other ofsaid valve elements to eifect corresponding actuation of said clutchmember.

16. In a machine tool of the type embodying a rotatable spindle and anelement translatable with respect to said spindle, transmission andcontrol mechanism for 'said parts including an actuator for the spindle,a controller for determining the coupling of "the actuator with the,

like and a prime mover for actuation of said transmission, of a clutchelement for operatively connecting the prime mover and said transmis-,

sion, power means ior eflecting shifting or the gears of saidtransmission to increase or decrease the rate transmittable thereby,driving means for said power shifter including a reverser, a firsthydraulic motor for eflecting disconnection of the transmission clutch,a second hydraulic motor for eiiecting opposite directional couplings ofthe reverser, a hydraulic control system for said motors including asource of actuating medium and a control valve intervening the motorshaving a first position eflfectiveto couple the source with the clutchmotor for effecting the driving of the transmission and having two additional, positions eiiective to couple the source with the reverser motorfor selective positioning of the reverser, said valve including portionscoupling the pressure source with the clutch motor to disconnect theclutch when the valve is in either of said additional positions, a firstmeans for positively shifting the, valve into its selected positions,and a remote hydraulic control means for effecting'independent shiftingof the valve into the additional reverser controlling positions.

19. The combination with an organized variable speed transmission for amachine tool or the like-and a prime .mover for actuation of saidspindle, an organized variable speed transmission ior actuation of thetranslatable member, clutch means for determining the operative couplingof.

said transmission, a power adjuster for said transmission, a hydrauliccontrol system for said parts including a source of actuating medium, ahydraulic motor for determining the position of the clutch, seriallydisposed valve elements intervening the source and motor, an actuatorfor shifting one of said valve elements to actuate the motor fordisconnection of the clutch, control means for the power adjuster, meansin the valve to selectively couple the source with the controltransmission, of a clutch element for operatively connecting the primemover and said transmission, power means for effecting shifting of thegears of said transmission to increase or decrease the ratetransmittable thereby, driving means for said power shifter including areverser, a first hydraulic motor for efiecting disconnection of thetransmission clutch, a second hydraulic motor for eifectingopposite'directional couplings of the reverser, a hydraulic controlsystem for said motors including a source of actuating medium and acontrol valve;intervening the motors having a first position eifectiveto couple the source with the clutch motor for effecting the driving'oithe verser controlling positions, an additional control valveintervening the source and the clutch motor, and means independent ofthe first valve and its controls for actuating the second valve tooperate the clutch motor for disconnection of the clutch.

LESTER F. NENNINGER, FRED A. HASSMAN.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 1,693,446 Kearney Nov. 27, 19281,845,844 Korsmo Feb. 16, 1932 1,914,167 Romaine et a1 June 13, 19331,919,150 Nenninger July 18, 1933 1,961,129 DeHaas et a1 June 5, 19341,978,354 Nenninger et al. Oct. 23, 1934 2,008,983 Kearney July 23, 19352,053,886 Williams Sept. 8, 1936 2,164,884 Nenninger et a1 July 4, 19392,202,766 Trosch May 28, 1940 2,349,595 Martelloti May 23, 19442,389,627 LeBlond et al Nov, 27, 1945

